Governor

ABSTRACT

A governor control valve wherein governor outlet pressure is regulated by exhausting fluid from an exhaust port in response to changes in centrifugal force based on vehicular speed changes. The device includes a shaft having a restricted main line pressure inlet, a governor pressure outlet and an exhaust port formed therein and an axial passage therebetween. A cylindrical pin mounted on the shaft supports both a concentric drive gear and one or more weight members suspended from the pin and transmits the torque from the drive gear to the shaft. One embodiment provides two separate governors in one assembly, one with a slow rising pressure curve, the other with a fast rising pressure curve. Another embodiment thereof provides a two-stage governor pressure vs. speed relationship. The first embodiment of the valve assembly consists of dual inlet, outlet and exhaust ports and passages, with a relief valve for each exhaust port, and two weights having different sizes and shapes suspended from two pins for respectively variably controlling the fluid exhaust through the exhaust ports past the relief valves, in response to centrifugal force. The second embodiment of the valve assembly consists of a single inlet and governor pressure outlet arrangement wherein fluid exhaust is controlled by one ball relief valve which is actuated by two different weight members suspended from one pin, the lighter weight member being in direct contact with the valve while the heavier weight member influences the lighter member through a spring until the heavier member contacts a stop.

United States Patent lnventor Erkki A. Koivunen Livonia, Mich. App]. No.782,943 Filed Dec. 11, 1968 Patented Feb. 2, 1971 Assignee GeneralMotors Corporation a corporation of Delaware GOVERNOR 14 Claims, 6Drawing Figs.

US. Cl. 137/54, 137/56, 73/537, 73/539, 73/540 Int. Cl. G05d 13/10 FieldofSearch 137/53, 47, 54, 56; 73/535, 537-540, 544, 550

References Cited UN lTED STATES PATENTS 3,035,592 5/1962 Kahn 137/543,133,552 5/1964 Newburgh l37/54X 3,242,936 3/1966 Kalb 137/54X3,413,991 12/1968 Lewicki 137/54 Primary Examiner-Clarence R. GordonAttomeys-E. W. Christen, A. M. Heiter and John Moran ABSTRACT: Agovernor control valve wherein governor outlet pressure is regulated byexhausting fluid from an exhaust port in response to changes incentrifugal force based on vehicular speed changes. The device includesa shaft having a restricted main line pressure inlet, a governorpressure outlet and an exhaust port formed therein and an axial passagetherebetween. A cylindrical pin mounted on the shaft supports both aconcentric drive gear and one or more weight members suspended from thepin and transmits the torque from the drive gear to the shaft. Oneembodiment provides two separate governors in one assembly, one with aslow rising pressure curve, the other with a fast rising pressure curve.Another embodiment thereof provides a two-stage governor pressure vs.speed relationship. The first embodiment of the valve assembly consistsof dual inlet, outlet and exhaust ports and passages, with a reliefvalve for each exhaust port, and two weights having different sizes andshapes suspended from two pins for respectively variably controlling thefluid exhaust through the exhaust ports past the relief valves, inresponse to centrifugal force. The second embodiment of the valveassembly consists of a single inlet and governor pressure outletarrangement wherein fluid exhaust is controlled by one ball relief valvewhich is actuated by two different weight members suspended from onepin, the lighter weight member being in direct contact with the valvewhile the heavier weight member influences the lighter member through aspring until the heavier member contacts a stop.

PATENTEU FEB zlsn 3,559,661.

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frkkz' 6?. H01 vunen ATTORNEY GOVERNOR This invention relates toautomatic transmissions for motor vehicles and more particularly to agovernor control valve for same.

In a conventional control system for a vehicle transmission having twoor more gear ratios engageable by hydraulically operated brakes andclutches, the automatic selection of the desired drive is in partdependent upon transmission output shaft speed or the driving speed ofthe vehicle, in order to operate the vehicle efficiently. Two types ofgovernors are currently being used, namely, two-stage governors andtwopressure governors.

A primary object of this invention is to provide an improved governorcontrol valve which provides a two-phase governor pressure curve.

Another object of this invention is to provide an improved governorwhich provides a two-stage governor pressure curve.

A further object of the invention is to provide a governor control valvewhich is simple in construction, economical to manufacture and efficientin operation.

A more specific object of the invention is to provide a governor valvewhich includes a shaft and a pair of relief valves respectivelycontrolled by primary and secondary weight members rotatably supportedon the shaft for obtaining the two pressures having different rates ofpressure rise.

Another object of the invention is to provide a governor valve havingone relief valve controlled by primary and secondary weight membersrotatably supported on a shaft and controlling the relief valve toobtain a governor pressure varying in two phases with speed.

Other objects and advantages of the invention will become more apparentwhen reference is made to the following description and accompanyingdrawings wherein:

FIG. 1 is a cross-sectional view of a governor control valve assemblyembodying the invention;

FIG. 2 is a cross-sectional view taken along the plane of line 2-2 ofFIG. 1, as if FIG. 1 were a full round view, and looking in thedirection of the arrows;

FIG. 3 is a perspective view of portions of FIG. 1;

FIG. 4 is a graph illustrating a typical curve of governor pressurevariation with speed; and

FIGS. 5 and 6 are fragmentary cross-sectional views illustratingmodifications of the invention.

Referring now to the drawings in greater detail, FIG. 1 illustrates agovernor control valve assembly 10, including a shaft 12 which isrotatably mounted at its ends 13 and 14 in suitable housings 16 and 18,respectively. Axially aligned passages 20 and 21 are formed in the shaft12, separated by a wall 22. A cavity 23 is formed in the housing 16adjacent the upper end 13 of the shaft 12 forming a chamber with theaxial passage 20, and a transverse opening 24 is formed in the lower end14 of the shaft 12 forming a chamber with axial passage 21. A regulatedfluid pressure supply is connected to inlet passages 26 and 27 formed inthe housings 16 and 18. Fluid flows through or downstream of orifices orrestrictions 28 and 29 to the first governor pressure chamber,comprising cavity 23 and passage 20 and the second governor pressurechamber provided by the transverse opening 24 and passage 21,respectively. Governor pressure outlets 30 and 31 are also formed in thehousings 16 and 18. Recesses or grooves 32 and 33 are formed on theopposite sides of the shaft 12, perpendicular to the axis thereof andintermediate the ends 13 and 14 thereof. The recesses 32 and 33 aresuitable for the insertion of pins 34 and 36, as will now be explained.

A substantially U-shaped weight member 38 (FIGS. 2 an 3), having ears orprojections 40 formed on each of the top edges of opposing sides thereofis disposed around the shaft 12 and pivotably mounted on the pin 34through openings 42 formed in the oppositely disposed projections 40.

A second substantially U-shaped weight member 44, having ears orprojections 46 formed on opposite upper edges thereof, includessidewalls longer, thicker and, therefore, heavier than those of thefirst-mentioned weight member 38. The member 44 is mounted around theshaft 12 on the second pin 36 adjacent the first weight member 38 bymeans of openings 48 fonned in the projections 46. Once the pins 34 and36 are slidably mounted in the openings 42 and 48, respectively, theends of the pins are staked, as illustrated in FIG. 2.

Each of the weight members 38 and 44 has a narrow tab 50 and 52,respectively, extending from one of the side edges thereof into cutoutportions of the other weight member and bending inwardly (FIG. 2). Thetab 52 on the longer weight member 44 is formed near the upper edgesthereof, while the tab 50 on the shorterweight member 38 is formed nearthe lower edges in FIG. 1, varying the distance each is away from itspivot point, determined by the pins 34 and 36. As may be observed in thedrawing, the tabs 50 and 52, being formed in the manner just described,are positioned axially adjacent to one another on opposite sides of theshaft 12. Radially aligned with each of the tabs 50 and 52 are openings54 and 55, including valve seats 56 and 57, respectively, formed in thewall of the shaft 12. Ball relief valves 58 and 60 are mounted in theopenings 54 and 55, respectively, their centers aligned with themidpoint of the tabs 50 and 52. The relief valves 58 and 60 could, ofcourse, be conical or disc-shaped, if desired.

After the weight member 38 and pin 34 subassembly and the weight member44 and pin 36 subassembly are mounted in the recesses 32 and 33 on theshaft 12, a cylindrical member 61 having exterior parallel cutoutportions 62 (FIG. 3) formed adjacent one end thereof and parallel slotsor grooves 64 formed through the body thereof perpendicular to thecutout portions 62, is slidably mounted on the shaft 12 such that theslots 64 sit on the pins 34 and 36 and the cutout portions 62 permitpivotal movement of the projections 40 and 46 of the members 38 and 44,respectively, while retaining the members 38 and 44 in their propersuspended positionson'the pins 34 and 36. When assembled, the spacingbetween tabs 50 and 52 and the base of the U-shaped weight members 38and 44 is such that balls 58 and 60 cannot fall out of seat bores 56 and57.

Gear teeth 66 are formed on the exterior of the member 61.

The member 61 and its associated teeth 66 are formed of any suitablematerial, such as nylon. The teeth 66 mesh with a conventionalspeedometer drive gear 68 rotatably connected to a transmission outputshaft 70.

OPERATION The operation of the governor control valve 10 will now bedescribed and related to the FIG. 4 graph.

Fluid at line pressure is supplied via the inlet 26, the orifice 28 andthe chamber 23 to the central passageway 20, while the same linepressure is supplied via the orifice 29, the inlet 27 and the transversepassage 24 to the central passageway 21.

As the transmission output shaft 70 rotates, the associated gear 68will, in turn, rotate the drive gear 66. As indicated above, thegovernor shaft 12 and the weights 38 and 44 will be rotated by the gear66, the torque being transmitted thereto by the pins 34 and 36.

At zero speed of the shaft 12, the tabs 50 and 52 will be suspended attheir further most positions from seats 56 and 57. Once pressure isapplied to the passages 20 and 21, it will force the valves 58 and 60outwardly against the tabs 50 and 52, respectively.

At low speeds of the transmission output shaft 70 and, hence, of thegovernor shaft 12, the weight numbers 38 and 44 will begin pivotingunder the effect of centrifugal force about their respective pins 34 and36, progressively increasing the biasing force acting on the valves 58and 60 toward the seats 56 and 57, respectively, influencing thepressure which will be transmitted through the outlets 30 and 31 to al-2 shift valve (not shown) and a 2-3 shift valve (not shown),respectively.

Inasmuch as the member 44 is heavier than the member 38, and its tab 52is axially closer to its pivot pin 36 than the tab 50 of the member 38is to the pin 34, the membert44 will have a greater bias force at lowerspeeds and reach its outermost position under the action of centrifugalforce before the member 38 reaches its outer position. Outward movementis, of course, limited by the contact of the relief valves 58 and 60against their respective seats 56 and 57, at which time fluid exhausttherethrough is stopped. At this time, governor pressure equals linepressure.

With increasing speed and increasing bias of member 44, governorpressure vs. speed is represented by the curve A of FIG. 4 and thedotted line extension thereof, and the 12 shift valve will be afiectedthereby. Also with increasing speed and bias by weight 38, there isinward movement of the valve 58 toward the seat 56, caused by the inwardmovement of the tab 50, to control fluid exhaust so as to produce agovernor pressure increasing at a slower rate with speed, as representedby the curve OC of FIG. 4, and the 2-3 shift valve will be affectedthereby.

FIG. illustrates a modification of the invention, wherein all thoseelements which are the same as the elements of the FIG. 1 structure bearthe same reference numerals. The FIG. 5 embodiment represents astructural modification of the type of governor valve included in U.S.Pat. No. 3,321,056, issued on May 23, I967, in the name of F. J.Winchell, et al. The variations from the FIG. 1 structure include aprimary weight member 72 and a secondary weight member 74, each of whichis suspended from the single pin 34. The weight numbers 72 and 74include tabs 76 and 78, respectively. The tab 76 of the primary weightmember 72 is positioned adjacent the shaft 12, whereas the tab 78 of thesecondary weight member 74 is positioned adjacent a ball relief valve 80mounted in an opening 82 adjacent a valve seat 84 for controlling theexhaust of fluid from the passage 20.

A cylindrical member 86 is fixedly secured to the primary weight member72 on the side opposite the tab 76. The cylindrical member 86 extendsradially inwardly from the primary weight member 72 through an opening88 formed in the secondary weight member 74, providing means fortransferring the effect of centrifugal force on the primary weightmember 72 to the secondary weight member 74. A spring 90 is mountedbetween the secondary weight member 74 and a flange 92 formed on theinner end of the cylindrical member 86. The member 86 is fixed to weight72 and abuts shaft 12 so ball valve 80 cannot fall out of seat 84 in anyrotary position of weight 72. A projection 94 is formed at the lower endof the secondary weight member 74 and extends radially outwardlytherefrom toward the primary weight member 72, serving as a stop meansunder the force of the spring 90.

Insofar as the operation of the FIG. 5 structure is concerned, under theaction of centrifugal force, the heavier primary weight member 72 willpivot outwardly about the pin 34 in a clockwise direction in FIG. 5. Thelighter secondary weight member 74 will likewise pivot about the pin 34in a clockwise direction under the action of centrifugal force, and willbe additionally influenced by the heavier primary weight member 72through the spring 90, whose innermost end will move outwardly with theflange 92 of the cylindrical member The heavy weight member 72 providesa biasing force which increases with speed at a high rate slightly lessthan curve OA" of FIG. 4, and the member 86 and spring 90 transmit thisforce to the light weight member 74, which has a biasing forceincreasing at a very slow rate like curve 0C of FIG. 4 so the combinedbiasing force of the primary and secondary weight members on the valve80 provides a governor pressure in the line 30 as illustrated by thecurve 0A of FIG. 4. The break point A" is reached when movement ofweight 72, permitted by compression of spring 90, results in the tab 76of the primary weight member 72 contacting the shaft 12. Once thiscontact is made, the primary weight member 72 will have its outwardmovement terminated with increased shaft 12 speed. At this point, theforce from the heavier primary weight member 72 being transmittedthrough the spring 90 to the lighter secondary weight member 74 will nolonger increase with increased shaft speed. Increased speed will nowcause the secondary weight member 74 to continue to pivot outwardly,thereby continuing to increase the biasing force to effect the positionof ball relief valve relative to the seat 84. The graphical result ofthis phase is illustrated by curve AB" of FIG. 4. The resultant governorpressure will be communicated via the single passage 30 to both the 12and the 2-3 shift valves (not shown).

FIG. 6 illustrates another two-stage modification of the invention,wherein all those elements which are the same as the elements of theFIGS. 1 and/or 5 structures bear the same reference numerals. Thevariations from the FIGS. 1 and 5 structures include a single centralpassage or chamber having a single restricted inlet and an outlet, suchas elements 26, 28 and 30 of FIG. 1, rather than the dual chambers 20and 21 of FIG. 1, with valves 102 and 104 being mounted adjacent seats106 and 108 in openings 110 and 112, respectively, both of whichcommunicate with the central chamber 100.

Primary and secondary weight members 114 and 116 are similar to theweight members 44 and 38 of FIG. 1 and include tabs 118 and 120positioned adjacent the valves 102 and 104, respectively. The weightmembers 114 and 116 also include bent end portions 122 and 124,respectively, which serve as stops against the shaft 12 to prevent theball valves 102 and 104 from falling out of the openings 110 and 112when there is no centrifugal force on the weights 114 and 116.

A spring 126 is mounted between a spring seat 128 formed on the outersurface of the shaft 12 and a seat 130 formed on the weight member 114,urging the tab 120 of the secondary weight 116 against the valve 104.The force of the spring 126 is such that the valve 104 will be heldagainst the seat 108 during low speed operation, resisting the pressureof the oil in the chamber 100, until such time as point A" is reached onthe two-stage curve of FIG. 4. The governor pressure curve 0A will bedetermined by the pressure of the fluid in the chamber 100 on the valve102 and exhausting therepast, forcing the valve 102 in a radiallyoutward direction in opposition to the progressively increasing effectof centrifugal force on the primary weight member 114, and hence, on thevalve 102. At a speed and corresponding governor pressure represented bypoint A, the effect of centrifugal force on the primary weight member114 will be such that the valve 102 will be forced closed by the tab 118against the pressure of the fluid in the chamber 100. At this point, thelatter pressure will be sufficient to overcome the combined force of thespring 126 and centrifugal force on the secondary weight member 116.Increased speed thereafter will, of course, cause the tab 120 to forcethe valve 104 toward the seat 108, thereby progressively increasinggovernor pressure as represented by the curve AB ofFIG. 4.

It should be apparent that the curves may be altered to suit otherapplications simply by changing the relative shapes and weights of theprimary and secondary pivotal weight members which control the fluidexhaust valves. If desired, it should also be apparent that springs, andthe like, may be incorporated in conjunction with the weight members 38and 44 to influence the governor pressure.

It should also be apparent that the governor shaft and dual or singlepin combination provides a novel means for supporting a drive gear andfor simultaneously pivotally suspending both weight members.

It should be further apparent that the dual control valve arrangementdescribed herein need not be limited to automatic transmissionapplications and could be used in any hydraulic or pneumatic applicationrequiring single, two-phase or twostage operation.

While but three embodiments of the invention have been disclosed anddescribed, other modifications thereof are possible.

I claim:

1. A governor for supplying a fluid pressure proportional to speed; arotary member having a chamber therein; a source of fluid underpressure; a restricted inlet passage connecting said source to saidchamber; an outlet passage connecting said chamber to exhaust having arelief valve member therein movable between an open and a closedposition for controlling flow from said chamber to exhaust and biased'byfluid pressure in said chamber to the open position, and weight meanspivotally mounted on said rotary member and being suspended therefrom toa position adjacent said relief valve member to open said relief valvemember in all rotary positions of said rotary member, at zero speed inresponse to gravity and to bias said relief valve to some regulatingposition between said open and said closed positions proportional tocentrifugal force to provide a governor pressure in said chamber varyingwith the speed of rotation of said rotary member.

2. A governor for supplying a fluid pressure proportional to speed; arotary member having a chamber therein, said rotary member being mountedfor rotation about an axis; a source of fluid under pressure; arestricted inlet passage connecting said source to said chamber; anoutlet passage connecting said chamber to exhaust having a relief valvemember therein movable between an open and a closed position forcontrolling flow from said chamber to exhaust and biased by fluidpressure in said chamber to the open position, said outlet passage beingsubstantially normal to said axis and having a valve seat therein, saidrelief valve member being reciprocally mounted in said inlet passage andhaving one side engaging said seat in said closed position; and weightmeans pivotally mounted on said rotary member and connected to saidrelief valve member to bias said relief valve to some regulatingposition between said open and said closed positions proportional tocentrifugal force to provide a governor pressure in said chamber varyingwith the speed of rotation of said rotary member, said weight meanshaving its center of mass on the side of said axis substantiallyopposite said outlet passage and relief valve member and having aportion extending beyond said relief valve member and engaging the otherside opposite said one side.

3. The invention defined in claim 1 and said weight means confining saidrelief valve member in said outlet passage in said closed position, saidoutlet passage having a seat limiting closing movement of said weightmeans and relief valve member in said closed position and said weightmeans and rotary member having stop means to prevent movement of saidweight means at said open position.

4. A governor for supplying controlled fluid pressure to a vehicletransmission having an output shaft, an output gear driven thereby, anda source of fluid under pressure, said governor comprising a rotatableshaft having a chamber formed therein, means for communicating saidfluid from said source to said chamber, and means operatively connectedto said rotatable shaft for varying the pressure of said fluid in saidchamber, said last-mentioned means including a pair of exhaust openingsformed in said shaft, a pair of valve means for controlling said pair ofexhaust openings, a pair of pin means operatively connected to saidrotatable shaft for rotation therewith, a weight member pivotallymounted on each of said pin means for controlling the movement of one ofsaid pair of valve means under the action of centrifugal force, biasingmeans mounted between said rotatable shaft and one of said weightmembers for urging the respective valve means toward a closed position,and gear means mounted on said pair of pin means around said rotatableshaft for rotating said rotatable shaft and for retaining said weightmembers in their respective positions on said pair of pin means, saidgear means being driven by said output gear.

5. A governor for supplying controlled fluid pressure to a vehicletransmission having an output shaft and an output gear driven thereby,said governor comprising a rotatable shaft, an axial passage formed insaid shaft, a source of fluid pressure for said axial passage, pin meansmounted on said shaft for rotation therewith, a weight member pivotallymounted on said pin means, a member including gear means mounted on saidpin means for retaining said weight member in position on said pin meansand for driving said rotatable shaft by means of said pin means, saidgear means being driven by said output gear, and valve means mounted onsaid shaft and having opening and closing movements thereon forexhausting fluid therethrough and thereby varying said pressure in saidaxial passage, said opening and closing movements of said valve meansbeing controlled by said weight member under the action of centrifugalforce.

6. A governor for supplying controlled fluid pressure to a vehicletransmission having an output shaft, an output gear driven thereby, anda source of fluid under pressure, said governor comprising a rotatableshaft having a chamber formed therein, means for communicating saidfluid from said source to said chamber, and means operatively connectedto said rotatable shaft for varying the pressure of said fluid in saidchamber, said last-mentioned means including an exhaust opening formedin said shaft, valve means for controlling said exhaust opening, pinmeans operatively connected to said rotatable shaft for rotationtherewith, a weight member pivotally mounted on said pin means forcontrolling the movement of said valve means under the action ofcentrifugal force, and gear means mounted on said pin means around saidrotatable shaft for rotating said rotatable shaft and for retaining saidweight member in position on said pin means, said gear means beingdriven by said output gear.

7. A compound governor for supplying controlled fluid pressure to avehicle transmission having an output shaft, an output gear driventhereby, and a fluid flow path, said governor comprising a rotatableshaft having two axial passages formed therein, means for communicatingsaid fluid flow path with said two axial passages, and means operativelyconnected to said rotatable shaft for varying the pressure of said fluidin said fluid flow path in accordance with two different pressure vs.speed curves, said last-mentioned means including first and secondexhaust openings formed in said shaft and communicating with said twoaxial passages, respectively, first and second valve means forcontrolling said first and second exhaust openings, first and secondsupport members operatively connected to said rotatable shaft forrotation therewith, first and second weight members pivotally mounted onsaid first and second support members, respectively, for variablycontrolling the movement of said first and second valve means under theaction of centrifugal force, and gear means mounted on said first andsecond support members around said rotatable shaft for rotating saidrotatable shaft and for retaining said first and second weight membersin position on said support members, said gear means being driven bysaid output gear.

8. The governor described in claim 7, wherein said support members arepins mounted in transverse grooves formed in said rotatable shaft.

9. A compound governor for supplying controlled fluid pressure to avehicle transmission having an output shaft, an output gear driventhereby, and a source of fluid under pressure, said governor comprisinga rotatable shaft having a pair of aligned axial passages formedtherein, means for communicating said fluid from said source to saidaligned axial passages, and means operatively connected to saidrotatable shaft for varying the pressure of said fluid in said alignedaxial passages in accordance with two different pressure vs. speedcurves, said last-mentioned means including first and second exhaustopenings formed in said shaft, each communicating with one of said pairof aligned axial passages, first and second relief valve means forcontrolling said first and second exhaust openings, first and second pinmembers operatively connected to said rotatable shaft for rotationtherewith, first and second weight members pivotally mounted on saidfirst and second pin members, respectively, for variably controlling themovement of said first and second valve means under the action ofcentrifugal force, and gear means mounted on said first and second pinmembers around said rotatable shaft for rotating said rotatable shaftand for retaining said first and second weight members in position onsaid pin members, said gear means being driven by said output gear.

10. The governor described in claim 9, wherein said first and secondrelief valve means are ball valves.

11. The governor described in claim 9, wherein said first and second pinmembers are mounted in recesses formed on opposite sides of saidrotatable shaft.

12. The governor described in claim 9, wherein said first and secondweight members each include three flat sides positioned in their freestate parallel to the axis of said rotatable shaft, a pair ofprojections extending upwardly from the top edges of two opposing sidesof each of said three flat sides, an opening formed in each of saidprojections for suspending said first and second weight members on saidpin members, and a tab extending from a side edge of one of each of saidthree flat sides, said tabs being positioned adjacent said first andsecond valve means.

13. The governor described in claim 9, wherein said gear means includesa cylindrical body having teeth formed around a portion of the peripherythereof, flat surfaces formed on opposite sides thereof spaced axiallyapart from said teeth, and a pair of notches formed therethroughperpendicular to said flat surfaces for mounting on said pin members.

14. A governor for supplying controlled fluid pressure to a vehicletransmission having an output shaft, an output gear driven thereby, anda source of fluid under pressure, said governor comprising a rotatableshaft having a chamber formed therein, means for communicating saidfluid from said source to said chamber, and means operatively connectedto said rotatable shaft for varying the pressure of said fluid in saidchamber, said last-mentioned means including an exhaust opening formedin said shaft, valve means for controlling said exhaust opening, a pinoperatively connected to said rotatable shaft for rotation therewith, apair of speed-responsive weight members pivotally mounted on said pinfor controlling the movement of said valve means under the action ofcentrifugal force, mounting means secured to the heavier of said pair ofspeedresponsive weight members and extending radially inwardlytherefrom, biasing means mounted between the innermost end of saidmounting means and the inner side of the lighter of said pair ofspeed-responsive weight members, a tab on said heavier weight memberadjacent said rotatable shaft for at times abutting against said shaft,and a tab on said lighter weight member adjacent said valve means.

1. A governor for supplying a fluid pressure proportional to speed; arotary member having a chamber therein; a source of fluid underpressure; a restricted inlet passage connecting said source to saidchamber; an outlet passage connecting said chamber to exhaust having arelief valve member therein movable between an open and a closedposition for controlling flow from said chamber to exhaust and biased byfluid pressure in said chamber to the open position, and weight meanspivotally mounted on said rotary member and being suspended therefrom toa position adjacent said relief valve member to open said relief valvemember in all rotary positions of said rotary member, at zero speed inresponse to gravity and to bias said relief valve to some regulatingposition between said open and said closed positions proportional tocentrifugal force to provide a governor pressure in said chamber varyingwith the speed of rotation of said rotary member.
 2. A governor forsupplying a fluid pressure proportional to speed; a rotary member havinga chamber therein, said rotary member being mounted for rotation aboutan axis; a source of fluid under pressure; a restricted inlet passageconnecting said source to said chamber; an outlet passage connectingsaid chamber to exhaust having a relief valve member therein movablebetween an open and a closed position for controlling flow from saidchamber to exhaust and biased by fluid pressure In said chamber to theopen position, said outlet passage being substantially normal to saidaxis and having a valve seat therein, said relief valve member beingreciprocally mounted in said inlet passage and having one side engagingsaid seat in said closed position; and weight means pivotally mounted onsaid rotary member and connected to said relief valve member to biassaid relief valve to some regulating position between said open and saidclosed positions proportional to centrifugal force to provide a governorpressure in said chamber varying with the speed of rotation of saidrotary member, said weight means having its center of mass on the sideof said axis substantially opposite said outlet passage and relief valvemember and having a portion extending beyond said relief valve memberand engaging the other side opposite said one side.
 3. The inventiondefined in claim 1 and said weight means confining said relief valvemember in said outlet passage in said closed position, said outletpassage having a seat limiting closing movement of said weight means andrelief valve member in said closed position and said weight means androtary member having stop means to prevent movement of said weight meansat said open position.
 4. A governor for supplying controlled fluidpressure to a vehicle transmission having an output shaft, an outputgear driven thereby, and a source of fluid under pressure, said governorcomprising a rotatable shaft having a chamber formed therein, means forcommunicating said fluid from said source to said chamber, and meansoperatively connected to said rotatable shaft for varying the pressureof said fluid in said chamber, said last-mentioned means including apair of exhaust openings formed in said shaft, a pair of valve means forcontrolling said pair of exhaust openings, a pair of pin meansoperatively connected to said rotatable shaft for rotation therewith, aweight member pivotally mounted on each of said pin means forcontrolling the movement of one of said pair of valve means under theaction of centrifugal force, biasing means mounted between saidrotatable shaft and one of said weight members for urging the respectivevalve means toward a closed position, and gear means mounted on saidpair of pin means around said rotatable shaft for rotating saidrotatable shaft and for retaining said weight members in theirrespective positions on said pair of pin means, said gear means beingdriven by said output gear.
 5. A governor for supplying controlled fluidpressure to a vehicle transmission having an output shaft and an outputgear driven thereby, said governor comprising a rotatable shaft, anaxial passage formed in said shaft, a source of fluid pressure for saidaxial passage, pin means mounted on said shaft for rotation therewith, aweight member pivotally mounted on said pin means, a member includinggear means mounted on said pin means for retaining said weight member inposition on said pin means and for driving said rotatable shaft by meansof said pin means, said gear means being driven by said output gear, andvalve means mounted on said shaft and having opening and closingmovements thereon for exhausting fluid therethrough and thereby varyingsaid pressure in said axial passage, said opening and closing movementsof said valve means being controlled by said weight member under theaction of centrifugal force.
 6. A governor for supplying controlledfluid pressure to a vehicle transmission having an output shaft, anoutput gear driven thereby, and a source of fluid under pressure, saidgovernor comprising a rotatable shaft having a chamber formed therein,means for communicating said fluid from said source to said chamber, andmeans operatively connected to said rotatable shaft for varying thepressure of said fluid in said chamber, said last-mentioned meansincluding an exhaust opening formed in said shaft, valve means forcontrolling said exhaust opening, pin means operatively connected tosaid rotatable shaft for Rotation therewith, a weight member pivotallymounted on said pin means for controlling the movement of said valvemeans under the action of centrifugal force, and gear means mounted onsaid pin means around said rotatable shaft for rotating said rotatableshaft and for retaining said weight member in position on said pinmeans, said gear means being driven by said output gear.
 7. A compoundgovernor for supplying controlled fluid pressure to a vehicletransmission having an output shaft, an output gear driven thereby, anda fluid flow path, said governor comprising a rotatable shaft having twoaxial passages formed therein, means for communicating said fluid flowpath with said two axial passages, and means operatively connected tosaid rotatable shaft for varying the pressure of said fluid in saidfluid flow path in accordance with two different pressure vs. speedcurves, said last-mentioned means including first and second exhaustopenings formed in said shaft and communicating with said two axialpassages, respectively, first and second valve means for controllingsaid first and second exhaust openings, first and second support membersoperatively connected to said rotatable shaft for rotation therewith,first and second weight members pivotally mounted on said first andsecond support members, respectively, for variably controlling themovement of said first and second valve means under the action ofcentrifugal force, and gear means mounted on said first and secondsupport members around said rotatable shaft for rotating said rotatableshaft and for retaining said first and second weight members in positionon said support members, said gear means being driven by said outputgear.
 8. The governor described in claim 7, wherein said support membersare pins mounted in transverse grooves formed in said rotatable shaft.9. A compound governor for supplying controlled fluid pressure to avehicle transmission having an output shaft, an output gear driventhereby, and a source of fluid under pressure, said governor comprisinga rotatable shaft having a pair of aligned axial passages formedtherein, means for communicating said fluid from said source to saidaligned axial passages, and means operatively connected to saidrotatable shaft for varying the pressure of said fluid in said alignedaxial passages in accordance with two different pressure vs. speedcurves, said last-mentioned means including first and second exhaustopenings formed in said shaft, each communicating with one of said pairof aligned axial passages, first and second relief valve means forcontrolling said first and second exhaust openings, first and second pinmembers operatively connected to said rotatable shaft for rotationtherewith, first and second weight members pivotally mounted on saidfirst and second pin members, respectively, for variably controlling themovement of said first and second valve means under the action ofcentrifugal force, and gear means mounted on said first and second pinmembers around said rotatable shaft for rotating said rotatable shaftand for retaining said first and second weight members in position onsaid pin members, said gear means being driven by said output gear. 10.The governor described in claim 9, wherein said first and second reliefvalve means are ball valves.
 11. The governor described in claim 9,wherein said first and second pin members are mounted in recesses formedon opposite sides of said rotatable shaft.
 12. The governor described inclaim 9, wherein said first and second weight members each include threeflat sides positioned in their free state parallel to the axis of saidrotatable shaft, a pair of projections extending upwardly from the topedges of two opposing sides of each of said three flat sides, an openingformed in each of said projections for suspending said first and secondweight members on said pin members, and a tab extending from a side edgeof one of each of said three flat sides, said tabs being positionedadjacent said first and second valve means.
 13. The governor describedin claim 9, wherein said gear means includes a cylindrical body havingteeth formed around a portion of the periphery thereof, flat surfacesformed on opposite sides thereof spaced axially apart from said teeth,and a pair of notches formed therethrough perpendicular to said flatsurfaces for mounting on said pin members.
 14. A governor for supplyingcontrolled fluid pressure to a vehicle transmission having an outputshaft, an output gear driven thereby, and a source of fluid underpressure, said governor comprising a rotatable shaft having a chamberformed therein, means for communicating said fluid from said source tosaid chamber, and means operatively connected to said rotatable shaftfor varying the pressure of said fluid in said chamber, saidlast-mentioned means including an exhaust opening formed in said shaft,valve means for controlling said exhaust opening, a pin operativelyconnected to said rotatable shaft for rotation therewith, a pair ofspeed-responsive weight members pivotally mounted on said pin forcontrolling the movement of said valve means under the action ofcentrifugal force, mounting means secured to the heavier of said pair ofspeed-responsive weight members and extending radially inwardlytherefrom, biasing means mounted between the innermost end of saidmounting means and the inner side of the lighter of said pair ofspeed-responsive weight members, a tab on said heavier weight memberadjacent said rotatable shaft for at times abutting against said shaft,and a tab on said lighter weight member adjacent said valve means.